DE2818439A1 - Drive for reciprocating sliding door - has worm and wheel unit with axial flexible spring absorbing shocks - Google Patents

Abstract

The drive for door and barriers is used especially for sliding reciprocating doors. The motor is connected to a worm and wheel drive of the door system. At least the worm (8) of the drive (6) is held axially in bearing for shock damping. This worm is in contact with a restoring spring (12) and can be preferably connected rigidly and coaxially with the rotor shaft (10). This whole unit rests axially against one or more restoring elements. The worm (8) and the rotor shaft (10) can be made as an integral unit.

Description

Drive for doors and the like

The invention relates to a drive for doors, barriers and the like, especially for swing doors, with an electric motor, which is preferably a lockable Motor is designed, as well as with a transmitting in both directions of power flow Gear, in particular a worm gear, which is connected to the element to be moved is in drive connection.

Such drives are already known.

For example, they are used in swing doors using induction loops activated when a vehicle, e.g.

a fork lift truck or the like approaches the door. Occasionally comes the doors, e.g.

due to power failure or malfunctions within the control circuit, not open so that the door is "driven open" by the vehicle. Do this, in particular due to the high gear reduction, considerable loads within the drive on what must be taken into account when dimensioning the drive to avoid damage In a disadvantageous way, therefore, the drive must be correspondingly stable and be voluminous.

We already know drives that are used to avoid shock overloads of the transmission have a slip clutch or the like. In a disadvantageous way are these Slipping clutches, however, a comparatively fast one Subject to wear and tear. They are also suitable for drives that have a lockable Motor (torque motor) have, not quite suitable.

The object of the invention is therefore to provide a drive of the type mentioned at the beginning Type that has a high drive torque and the short-term, In particular, absorb shock loads on the output side without risk of damage can. The drive should have a comparatively small design.

To solve this problem, it is proposed according to the invention in particular that that at least the worm of the gear axially against at least one restoring element is mounted displaceably in terms of shock absorption.

In the first moment of the shock load, the worm can counteract this the force of the restoring element to give way axially, so that the load shock damped and thereby also the load on the transmission is significantly reduced.

In addition, this also reduces the breakaway torque between the worm wheel and the worm favored because between the interlocking Tooth flanks of the worm wheel and the worm a relative sliding movement to one another occurs. During the thrusting movement, the screw is driven by the Worm gear, like a rack, initially axially against the force of the return elements shifted, with the transition to rotary motion due to the sliding motion that occurs the screw is favored or takes place with a low force impulse load. In advantageous Thus, the transmission can be constructed comparatively small and nevertheless withstand high impact loads.

A preferred embodiment provides that the screw preferably is rigidly and coaxially connected to the rotor shaft and that this unit as a whole is axially displaceable against one or more restoring elements. These Embodiment is easy to manufacture and also has the advantage that the motor rotor by its mass acts as a damping element.

The worm or the worm with rotor are expediently axial slidable in both directions against one or more return elements stored. As a result, shock loads can occur in both directions of rotation of the output shaft be absorbed attenuated what z. B. is desirable for swing doors.

Advantageously, springs can be used as restoring elements, preferably Compression springs, in particular disc springs, are used.

These can advantageously be used on both end faces of the rotor attacking while sitting on the rotor shaft and on the other hand against the motor housing prop up.

As an additional shock overload protection, it can be advantageous to when the transmission path between the output shaft and the worm wheel is a Has overload clutch. This overload clutch can then expediently so be set so that they are at shock loads that occur in spite of the shock power attenuation pose a risk of damage to the gearbox.

One embodiment of this overload clutch provides that this is designed as a latching coupling, which is preferably depressions on the one hand as latching elements and on the other hand partially engaging, axially outwardly pressurized Has locking balls.

Additional refinements of the invention are set out in the further subclaims listed. The invention is explained in more detail below with reference to the drawings.

It shows: Fig. 1 a drive with motor and gear in section, 2 shows a somewhat schematic representation of a rotary stop, Fig. 3 shows a partially sectioned side view of a latching coupling, FIG. 4 shows a Top view of this locking coupling according to the section line IV - IV in Fig. 3 Fig. 5 a Side view and FIG. 6 shows a plan view of a somewhat modified one Locking coupling, FIG. 7 is a side view and FIG. 8 is a top view of a turn modified locking coupling.

A drive 1 in particular for swing doors and the like has a Motor 2 and a transmission 3, which are enclosed by a common housing 4 are. The motor 2 is designed as a lockable so-called torque motor, the can be blocked under power without being damaged. This has the advantage that switch, clutches and the like can be omitted with this door drive so that the operational safety is also increased thereby. Between the engine 2 and the output shaft 5, the gear 3 is arranged with high reduction to the to have the necessary large torque on the output shaft 5 available.

The transmission 3 is seen through essentially in the drive direction a worm gear 6 and formed by a downstream spur gear 7. The worm 8, which is covered here by the worm wheel 9, is rigid and coaxial preferably integrally connected to the rotor shaft 10.

According to the invention, the rotor shaft with the rotor sitting on it is now 11 and the worm 8 axially displaceable against return elements 12 in the sense of a Shock absorption stored.

In the exemplary embodiment, disc springs are used as restoring elements 12 13, on the one hand each against an end face of the rotor 11 and on the other hand support against the bearings 14 of the rotor shaft 10.

The worm wheel 9 sits on a shaft 15 at both ends is stored within the housing wall. Coaxial with the worm wheel 9 is non-rotatable connected to this, a pinion 16 is arranged, which is connected to the output shaft 5 connected gear 17 meshes. The output shaft 5 is also within the housing 4 stored twice. The free end of the output shaft 5 protrudes from the bottom of the housing and is connected to the elements to be moved, e.g. with swing doors or the like connectable. The transmission 3 is not designed as a whole to be self-locking, so that in both directions of force flow, i.e. from the motor to the output shaft as well as conversely, rotary movements can be transmitted from the output shaft to the motor. This also makes it possible, for example, to have swing doors connected to the drive also by hand, e.g. in the event of a power failure or if an automatic opening in the event of pedestrian traffic is not wanted, are easy to open.

In practice it happens that such swing doors or the like are hit by vehicles without the doors opening automatically. This can occur, for example, in the event of a power failure or malfunctions in the activation of the opening drive occurrence. With this approach to the doors, shock loads occur, which are significant are higher than the load on the drive during normal operation. To these burdens to be able to intercept is with the comparatively compact drive according to the invention 1 the aforementioned shock absorption through the axially displaceable bearings, The rotor 11 with a worm 8, which supports itself against the restoring elements 12, is provided. In the event of a jerky rotary movement of the output shaft 5, e.g. caused by a vehicle approaching a swing door connected to the output shaft 5, the rotary motion is transmitted to the worm wheel 9, and this then drives the screw and thus the rotor 11 on. Because of the jerky load on the one hand and the high gear ratio of the worm gear and the moment of inertia of the rotor 11 on the other hand, there is a considerable force component in the axial direction of the rotor shaft 10 on With a rigid mounting of this rotor shaft 10 would be inside the gear considerable forces practically occur through a "force back pressure".

On the other hand, in the case of the shock load absorption according to the invention in the first Moment of shock loading of the rotor with the worm 8 somewhat axially against the restoring force evade the disc springs 13, this axial displacement also being a better one Reduction of the static friction between the worm wheel 9 and the worm 8 causes. With this axial displacement, a sliding movement already occurs from the screw due to twisting of the worm wheel. This can advantageously the first peak load is absorbed and the transmission is overloaded be avoided.

The arrangement of the worm gear 6 directly behind the motor 2 with Coaxially arranged to the rotor worm is particularly advantageous because an axial Displacement of the screw 8 with this arrangement does not have any adverse effects on other drive or gear parts.

The restoring force of the restoring elements 12 and preferably also the axial displacement path of the rotor 11 with the worm 8 are expedient matched to the maximum shock load capacity of the gear unit. So you can through appropriate dimensioning of the springs and / or the displacement path (damping path) an adaptation to the shock loads that may occur and also to the Make the gearbox firm.

Fig. 1 also shows that the axial length of the rotor 11 is larger than that of the stator 18 and that the rotor 11 in its central position (Fig. 1) in particular on both sides of the stator 18 about the respective possible Displacement of the rotor 11 protrudes axially. This results in better thermal properties with displaced rotor 11. It should be noted that the rotor 11 is also in the end positions, where the motor is mechanically blocked, deflects somewhat axially. Through the aforementioned somewhat longer training of the rotor 11 compared to the stator 18, however, increases Current consumption of the motor 2 only slightly, since it is also axially displaced in this Position of the rotor the full length of the stator 18 faces the rotor.

Fig. 1 to 3 can still be seen that the output shaft 5 of the transmission 3 is rotatably connected to a stop lever 19, which in the end positions, such as for example in Fig. 2 drawn in dashed lines, on housing projections 20 or the like is present. In order to cushion the rotary movement at the stops 20, the Stop lever 19 on its stop surfaces 21 stop damper 22. As a stop damper 22 are used on the stop lever 19 in each case on its stop surfaces 21 protruding, cushioned stop elements 23. The spring 23 a is here by a pin 38 in the Lever 19 held.

In particular, FIGS. 3 and 4 show yet another measure to reduce overloads of the drive 1 to avoid. This is in addition to what is already prescribed Measures an overload clutch 24 is provided between the output shaft 5 and the gear 17 seated on it is arranged. This overload clutch 24 is designed as a locking clutch. For this purpose, the gear wheel sitting on the output shaft 5 is used 17 as a spur gear with a central recess 25 for receiving a coaxial coupling element 26 trained. The gear 17 is rotatably mounted on the output shaft 5 and the coupling element 26 is firmly connected to the output shaft 5 the gear 17 and the coupling element 26 are provided with locking elements. To do this, points the outer ring 27 of the gear 17 which delimits the recess 25, bores 28 and the coupling element 26 protruding radially beyond its outer end face 29, radially movable and outwardly force-loaded Locking balls 30 on. These locking balls 30 grip in the functional position in areas in the respective Hole 28 a. In the exemplary embodiment, 27 of the gear 17 are in the outer ring two diametrically arranged bores 28 and accordingly also two in the functional position locking balls 30 engaging in this are provided in the coupling element 26. Through this occurs, among other things, a symmetrical load on the coupling parts. the The clutch force of the overload clutch 24 can be applied to the practical needs. This can be done, for example, by different Depths of engagement of the locking balls 30 in the corresponding bores 28 by adaptation made of the spring forces and the like pressing the locking balls radially outward will. In the exemplary embodiment, the diameter of the bores 28 is approximately half that as large as the diameter of the locking balls 30. Also due to the number of used Locking elements, the coupling force can be of different sizes.

The above-described overload clutch 24 also has the essential The advantage of not having to adjust the angle of rotation after the clutch has been released is necessary because the locking elements after a corresponding defined rotation mesh again.

The drive 1 according to the invention described above is preferably suitable for doors, barriers and the like that should also be able to be moved by hand without that the drive must be disconnected or started.

A major advantage of this drive is its high Load capacity due to shock torsional loads occurring on the output shaft side at the same time comparatively small design. As a result, the drive 1 according to the invention can also can be used well in confined spaces. It also results from according to the invention enabled reduced dimensioning, in particular of the gearbox, a more cost-effective production.

A somewhat modified embodiment of an overload clutch 24a still show FIGS. 5 and 6. In this embodiment are inside in the outer ring 27 of the gear 17 axially oriented grooves 33 are provided in the radially outward spring loaded rollers 34 engage. Fig. 6 shows that there are twelve recesses 33 are provided. Depending on the desired response value of the overload clutch 24a there is the possibility of using one that is matched to the response value of the overload clutch Use number of locking bodies 34, these in pairs diametrically opposite each other are provided. Accordingly, with an overload clutch 24a, the already should respond to comparatively low loads, two locking bodies 32 are provided, as shown in FIG. At higher load values, the number of Latching body 32 corresponding to up to twelve latching bodies 32 in the exemplary embodiment (Fig. 6) increase. The same applies to the overload clutch 24 according to FIG.

3 and 4.

Another modified embodiment of an overload clutch Figures 7 and 8 show 24b. Here the spur gear 17 is coaxial Locking plate 31 rotatably connected. This locking plate 31 has axially protruding Locking teeth 35 (Figure 8), which are arranged in an outer ring area. Even the coupling element 26 has in this embodiment example on its the locking plate 31 facing side an engaging in the locking teeth 35 counter teeth with locking teeth 35a. The gear 17 and the locking plate 31 connected to it are somewhat axial slidable on the output shaft 5 and axially to the coupling element 26 spring-loaded by a plate spring 36. This plate spring 36 is supported on the axially fixed bearing 37. When the clutch is overloaded 24 b gives way to the gear 17 with its locking plate 31 axially downward against the spring force the spring 36 so that the locking teeth 35 and 35a disengage. The ratchet teeth 35 and 35a have inclined side flanks.

It should also be mentioned that the output shaft 5 also on both sides from the Housing 4 can be led out, as indicated by dashed lines in FIG. 1. This can be done, for example, when using the drive 1 according to the invention for Barriers and the like. Be advantageous.

This results in an approximately symmetrical one for the shaft 5 and its mounting Load. In addition, this means that the drive can, if necessary, also be installed in different positions can be used.

All shown in the description, the claims and the drawing Features can be essential both individually and in any combination with one another Have meaning.

- Expectations -

Claims (21)

Claims fo drive for doors, barriers and the like, in particular for swing doors, with an electric motor, which is preferably a lockable motor is designed, as well as with a transmission transmitting in both directions of force flow, in particular a worm gear, which is in drive connection with the element to be moved it says that at least the screw (8) of the transmission (6) axially displaceable against at least one restoring element (12) is stored in terms of shock torsional load damping. 2. Drive according to claim 1, characterized in that the screw is preferably rigidly and coaxially connected to the rotor shaft (10) and that this The unit is axially displaceable as a whole against one or more restoring elements (12) is stored. 3. Drive according to claim 1 or 2, characterized in that the The worm (8) and the rotor shaft (10) are integrally formed. 4. Drive according to one or more of claims 1 to 3, characterized characterized in that the screw (8), or. the screw (8) with rotor (11), axially in both directions is mounted displaceably against one or more restoring elements (12), in particular from a middle position. 5. Drive according to one or more of claims 1 to 4, characterized characterized in that the restoring elements (12) are springs, preferably compression springs, in particular disc springs (13) are used. 6. Drive according to one or more of claims 1 to 5, characterized characterized in that the restoring force of the restoring elements (12) and preferably also the axial displacement of the rotor (11) or the worm (8) to the maximum The shock load capacity of the gearbox (3) are matched. 7. Drive according to one or more of claims 1 to 6, characterized characterized in that at both ends of the rotor (11) on the rotor shaft (10) Attack springs located, in particular disc springs (13), which on the other hand support against the motor housing. 8. Drive according to one or more of claims 1 to 7, characterized characterized in that the axial length of the rotor (11) is greater than that of the stator (18) and that the rotor is in the central position (Fig. 1), in particular on both sides of the stator (18) protrudes axially approximately by the respective displacement path of the rotor (11). 9. Drive according to one or more of claims 1 to 8, characterized characterized in that the output shaft (5) of the transmission (3) with a stop lever (19) is connected, which in the end positions on housing projections (20) or the like is present. 10. Drive according to claim 9, characterized in that the stop lever (19) on its stop surfaces (21) and / or optionally the housing projections (20) have stop damper (22). 11. Drive according to claim 10, characterized in that as a stop damper (22) on the stop lever (19) each protruding on its stop surfaces (21), Spring-loaded stop elements (23) are used. 12. Drive according to one or more of claims 1 to 11, characterized characterized in that coaxially to the worm wheel (9) a rotatably connected to this Pinion (14) is arranged, which is connected to a with the output shaft (5) Gear (17) meshes. 13. Drive in particular according to claim 1, characterized in that that the transmission path between the output shaft (5) and the worm wheel (9) has an overload clutch (24). 14. Drive according to claim 13, characterized in that the overload clutch (24) is designed as a latching coupling, which is preferably as latching elements on the one hand Depressions and on the other hand partially engaging therein, axially outwardly pressurized Locking body (32), e.g. locking balls (30), rollers, cones or the like. having. 15. Drive according to claim 13 or 14, characterized in that the gear (17) seated on the output shaft (5) as a spur gear with a central one Recess (25) designed to receive a coaxial coupling element (26) is that the gear (17) rotatably mounted on the output shaft (5) and the coupling element (26) is firmly connected to the output shaft (5) and that the coupling element (26) and the gearwheel (17) have the locking elements for rotational connection. 16. Drive according to claim 15, characterized in that the axial Depth of the recess (25) in the gearwheel (17) is approximately the axial thickness of the coupling element (26) corresponds to the outer ring (27) of the gearwheel which bounds the recess (25) (17) at least one radial recess, in particular a bore (28), one axial Groove (33) or the like and the coupling element (26) at least one radially over its outer end face (29) protruding, radially movable and subjected to an outward force, in the functional position, latching body engaging in regions in the recess (s) (32); 17. Drive according to one or more of claims 13 to 16, characterized characterized in that at least two diametrically arranged recesses in the outer ring (27) of the gearwheel (17) and two latching bodies that engage in the functional position (32) are provided in the coupling element (26). 18. Drive according to one or more of claims 13 to 17, characterized characterized in that the diameter of the recesses designed as bores (28) in the outer ring (2) is about half as large as the diameter of the locking balls (30) and compression springs are used to apply force to the balls. 19. Drive according to one or more of the preceding claims, characterized characterized in that approximately groove-shaped, preferably rounded in cross-section, axially oriented recesses (33) are provided that serve as locking bodies rollers (34) and that preferably in the outer ring (27) twelve recesses (33) and in the Coupling element, if necessary, two to twelve locking bodies (32) are provided. 20. Drive according to one or more of the preceding claims, characterized characterized in that the spur gear (17) rotatably with a coaxial locking plate (31) is connected, the locking teeth projecting axially at least in a ring area (35) has that the coupling element (26) on its facing the locking plate (31) Side has a counter toothing engaging in the ratchet teeth (35) and that the gear (17) with the locking plate (31) axially to the coupling element (26) movable and spring-loaded is. 21. Drive according to one or more of the preceding claims, characterized characterized in that the output shaft (5) in particular for symmetrical loading E.g. when used for a barrier drive, led out of the housing (4) on both sides is.